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EP3284976B1 - Support epicycloïdal - Google Patents

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Publication number
EP3284976B1
EP3284976B1 EP16184865.0A EP16184865A EP3284976B1 EP 3284976 B1 EP3284976 B1 EP 3284976B1 EP 16184865 A EP16184865 A EP 16184865A EP 3284976 B1 EP3284976 B1 EP 3284976B1
Authority
EP
European Patent Office
Prior art keywords
drive
planet carrier
cheek
input
hub
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16184865.0A
Other languages
German (de)
English (en)
Other versions
EP3284976A1 (fr
Inventor
Arno Klein-Hitpass
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Flender GmbH
Original Assignee
Flender GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=56740927&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP3284976(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Priority to DK20172987.8T priority Critical patent/DK3708878T3/da
Application filed by Flender GmbH filed Critical Flender GmbH
Priority to ES20172987T priority patent/ES2945582T3/es
Priority to ES16184865T priority patent/ES2806452T3/es
Priority to EP20172987.8A priority patent/EP3708878B1/fr
Priority to DK16184865.0T priority patent/DK3284976T3/da
Priority to EP23166461.6A priority patent/EP4219983A1/fr
Priority to EP16184865.0A priority patent/EP3284976B1/fr
Priority to CN201710707862.1A priority patent/CN107763196B/zh
Priority to US15/680,648 priority patent/US10465791B2/en
Publication of EP3284976A1 publication Critical patent/EP3284976A1/fr
Publication of EP3284976B1 publication Critical patent/EP3284976B1/fr
Application granted granted Critical
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
    • F16H1/2827—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the planet carrier, e.g. relative to its shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
    • F16H1/2836—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the planets relative to the planet carrier or by using free floating planets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/2863—Arrangements for adjusting or for taking-up backlash

Definitions

  • a planetary gear which has a planet carrier in which a plurality of planet gears is rotatably received.
  • the planet carrier has two cheeks, which are connected to each other by webs. Furthermore, a bushing is received in one of the cheeks, in which a bolt is in turn received.
  • the cheeks of the planet carrier have an inner and an outer section along their wall.
  • US 2012/0028756 A1 discloses a planet carrier which has two cheeks in which a planet pin is received.
  • a cheek of the planet carrier is left between the webs.
  • An eye for receiving the planet bolt is arranged in the region of the cutout and is molded onto the hub of the corresponding cheek. As a result, the planet pin is received at one end in a flexible eye.
  • the object of the present invention is to provide an improved planet carrier.
  • the planet carrier has a drive-side hub, a drive-side outer cheek, a driven-side cheek and at least one web connecting the two said cheeks.
  • the components of the planet carrier such as hubs, cheeks and axle seats of the planetary axis, are differentiated with the position determinations "on the drive side" and "on the output side”.
  • the output-side cheek has at least one output-side axle seat, each for an output-side end of a planetary axis.
  • the planet carrier also has a drive-side inner cheek, which is arranged parallel to the drive-side outer cheek and has at least one drive-side axle seat each for a drive-side end of a planetary axis.
  • a planetary axis can be inserted into corresponding axle seats, which are each arranged in the drive-side inner cheek and the driven-side cheek.
  • inner and outer cheek are defined by the fact that when the planet carrier is viewed along the axis of rotation R of the planet carrier from the drive side, the drive-side outer cheek is closer to the viewer than the drive-side inner cheek; the drive-side outer cheek is thus arranged in an “outer” region of the planet carrier, whereas, relative to this, the drive-side inner cheek is further arranged in an “inner” region of the planet carrier.
  • the drive-side inner cheek supports the drive-side planet axle ends via the planetary axle seats, the drive-side outer cheek is connected to the webs. The webs are also connected to the driven side cheek.
  • the planet carrier On the drive side, the planet carrier has two cheeks, an inner and an outer.
  • the inner cheek on the drive side is arranged between the outer cheek on the drive side and the cheek on the output side. Due to the parallelism of the drive-side outer and inner cheek, the planet carrier according to the invention offers the possibility of adjusting the torsional rigidity of the inner load path, which leads from the drive-side hub to the drive-side axle seat, to the torsional rigidity of the outer load path, which leads from the drive-side hub to the drive-side axle seat to be adjusted so that a defined relative rotation of the drive-side axle seat to the output-side axle seat occurs under load. With an optimal adjustment, the two axle seats rotate by the same amount, so that the planetary axis is not misaligned under load.
  • the invention provides a planet carrier which is relatively light and whose cheeks hardly or not at all twist relative to one another under load.
  • the invention is based on the knowledge that the planet carrier is a torsion spring from a structural mechanical point of view, i.e.
  • a torsion spring is:
  • the seats of the planetary axes in the two cheeks are connected to each other by a torsion spring.
  • a rotation of the planet carrier cheeks occurring under load and the resulting misalignment of the planetary axis can thus only be varied by varying the torsional stiffness of this torsion spring.
  • the load path means that Path on which the forces due to an external load are conducted from the drive side through the planet carrier to the output side.
  • the torsional stiffness of the outer (“long”) load path is primarily determined by the thickness and width of the webs and the size of the openings for the planet gears, i.e. influences the shape of the webs, the thickness of the cheeks and the diameter of the drive-side hub.
  • the torsional stiffness of the inner (“short”) load path is primarily influenced by the diameter and the thickness of the drive-side inner cheek and its constructive connection with the planet carrier.
  • the load path to the second torque derivation point, ie the planetary axle seats on the output side is parallelized such that the torsional stiffnesses of the two paths can be varied separately from one another.
  • the drive-side inner cheek is fastened to the drive-side hub and / or to the drive-side outer cheek and / or to the at least one web.
  • both drive-side cheeks are connected to the drive-side hub.
  • a relatively long load path is available to match the load path of the second, axle-side axle seat.
  • An advantage in the case of an attachment The drive-side outer cheek ensures that cast or welded components have good accessibility for cleaning the transitions.
  • cast or welded components have good accessibility for cleaning the transitions. Furthermore, smaller wall thicknesses are sufficient in this case.
  • the torsional stiffness of the inner load path which leads from the drive-side hub to the drive-side axle seat, is matched to the torsional stiffness of the outer load path, which leads from the output-side hub to the drive-side axle seat, in such a way that a load occurs sets defined relative rotation of the drive-side axle seat to the output-side axle seat.
  • the planet carrier is used according to the invention for wind power transmissions. This is an advantage because in wind turbines very high torques are introduced from the drive side (rotor side) into the planet carrier.
  • the planet carrier consists of several parts. It is possible that the planet carrier is assembled from several individual parts by welded connections or screw connections. The advantage of a combination of several components is that the manufacture of the drive-side cheeks is facilitated.
  • the planet carrier is assembled from several individual parts by means of welded connections, at least along a partial length the weld connections relief notches are arranged.
  • one or more individual parts are simple cylindrical or disk-shaped elements.
  • the base body of the planet carrier i.e. the element having the webs can be formed from a central tube with cutouts for the planets.
  • the drive-side hub can be connected to the central tube via a torsion washer. All welds are preferably welded through and closed. Preferably the welds are circular, i.e. there are no notches in the weld.
  • the weld seams are preferably placed in such a way that they lie in relatively low-stress areas.
  • any number of planets can be stored in the planet carrier.
  • Usual planet gears have three or four planets. However, fewer than three or more than four planet gears can also be used in the planet carrier.
  • All cheeks can have any geometry, e.g. be designed as solid disks, spoke wheels or curved disks.
  • the cheeks in particular the inner cheek on the drive side, can have constrictions and / or openings between the axle seats, the design parameters such as number, position, size, shape, etc. of which can influence the torsional rigidity of the cheeks.
  • the planet carrier can be made of any material, e.g. made of cast iron, steel or plastics, in particular glass fiber reinforced plastics (GRP or CFRP).
  • GRP glass fiber reinforced plastics
  • Fig. 1 shows a conventional two-cheek planet carrier.
  • the drive-side hub 1 is also referred to as a long hub.
  • On the outer diameter of the drive-side cheek 2 webs 4 are arranged, which are designed as an axially extending tube provided with openings 3.
  • the webs 4 connect the drive-side cheek 2 to a driven-side cheek 5, which is also designed as a radially running disk.
  • An output-side hub 7 is arranged on the inside diameter of the output-side cheek 5, which is designed as an axially extending pipe stub.
  • the hub 7 on the output side is also referred to as a short hub.
  • the planet carrier is in a gearbox about its axis of rotation R rotatably by the two hubs 1, 7 by means of bearings, be it roller or slide bearings, supported against the gear housing.
  • Axially aligned bores 6a, 6b are made in each of the two cheeks 2, 5 and form seats for planet axes, on which planet gears are rotatably mounted.
  • a drive-side end of a planetary axis is inserted into a drive-side axle seat 6a in the drive-side cheek 2 and a driven-side end of a planetary axis is inserted into an output-side axle seat 6b in the driven-side cheek 5.
  • a notch 11 is formed, at which stress peaks arise.
  • the webs 4 extend between the two cheeks 2, 5 and between the openings 3, through which the teeth of the planet gears protrude in order to mesh with a ring gear surrounding the planet carrier.
  • a sun gear is arranged in the axial center of the planet carrier, which also meshes with the planet gears.
  • the planet carrier can be arranged in a planetary gear such that a torque of a drive, for example a rotor shaft of a wind power plant, is brought to the drive-side hub 1.
  • the planet gears mesh with the ring gear and the centrally arranged sun gear in such a way that with a fixed ring gear rotation of the drive-side hub 1 leads to faster rotation of the central sun gear.
  • the rotation of the sun gear axis, on which the sun gear is arranged in a rotationally fixed manner, is output as an output, if necessary, to a further gear stage downstream of the planet carrier and then finally to a machine downstream of the gear, e.g. transfer a generator.
  • Fig. 2 shows a first embodiment of a planet carrier according to the invention.
  • the structure of the planet carrier according to the invention largely corresponds to that of the conventional planet carrier Fig. 1 , except for the drive-side cheek, which according to the invention is replaced by two drive-side cheeks 2a, 8 arranged in parallel.
  • the distinction between “inner” and “outer” cheek is defined by the fact that when the planet carrier is viewed along the axis of rotation R of the planet carrier from the drive side, ie in the representation of FIG Fig.
  • the drive-side outer cheek 2a is closer to the viewer than the drive-side inner cheek 8; thus the drive-side outer cheek 2a is arranged in the "outer” region of the planet carrier, whereas, relative to this, the drive-side inner cheek 8 is arranged further in the "interior" of the planet carrier.
  • the drive-side inner cheek 8 is fastened to the drive-side hub 1 via a drive-side inner hub 9.
  • the drive-side outer cheek 2a is fastened to the drive-side hub 1 via an drive-side outer hub 10.
  • the inner hub 9 on the drive side is an axially extending stub tube which is arranged closer to the axis of rotation R than the axially extending stub tube which forms the outer hub 10 on the drive side.
  • the drive-side axle seat 6a is arranged exclusively in the drive-side inner cheek 8.
  • the torsional stiffness of the outer (“long”) load path is primarily determined by the thickness and width of the webs 4 and the size of the openings 3 for the planet gears, i.e. influences the shape of the webs 4, the wall thickness of the outer cheek 2a, and the thickness and length of the drive-side outer hub 10.
  • the torsional rigidity of the inner (“short”) load path is primarily influenced by the diameter and the thickness of the inner hub 9 on the drive side.
  • the torsional rigidity of the inner load path, which leads from the drive-side hub 1 to the drive-side axle seat 6a, is matched to the torsional rigidity of the outer load path, which leads from the drive-side hub 1 to the drive-side axle seat 6b, in such a way that there is a load sets defined relative rotation of the drive-side axle seat 6a to the output-side axle seat 6b.
  • Fig. 3 shows the planet carrier according to Fig. 2 with a planet gear 12, a planetary axis 14, a bearing inner ring 13 and a planetary bearing 15.
  • the drive-side end of the planetary axis 14 is seated in the drive-side axle seat 6a, which is arranged in the drive-side inner cheek 8, while the output-side end of the planetary axis 14 in the output-side axle seat 6b sits, which according to the conventional planet carrier Fig. 1 is arranged in the output-side cheek 5.
  • Fig. 4 shows a further embodiment of a planet carrier according to the invention with hub bearings on both sides. It is compared to the in Fig. 2
  • the drive-side inner cheek 8 is not fastened to the drive-side hub 1 via an inner hub 9, but rather to the drive-side outer cheek 2a via an axial stub tube 8a.
  • Fig. 5 shows a further embodiment of a planet carrier according to the invention with hub bearings on both sides. It is compared to the in Fig. 2 In the embodiment shown, the drive-side inner cheek 8 is not attached to the drive-side hub 1 via an inner hub 9, but rather to the web 4, more precisely: to the drive-side half of the web 4.
  • Fig. 6 shows a further embodiment of a planet carrier according to the invention.
  • the structure of the planet carrier largely corresponds to that of the planet carrier according to the invention Fig. 2 , however, is missing according to the planet carrier Fig. 6 the output-side bearing in an output-side hub. Instead, the planet carrier is in accordance Fig. 6 on the drive-side hub 1 on one side, ie overhung.
  • Fig. 7 shows a further embodiment of a planet carrier according to the invention with one-sided storage.
  • the planetary axis projects so far beyond the driven-side cheek 5 on the output side that a planetary gear 17, which is clamped in between the ring gear and the sun gear, is accommodated on the planetary axis 14.
  • a planet gear 12 inserted between the drive-side cheeks 2a, 8 and the driven-side cheek 5 is mounted on the planetary axis 14.
  • Fig. 8 shows for better illustration of the invention a perspective view of a section of a planet carrier according to the invention, which in Fig. 2 Similar planet carrier shown, the planet axis 14 is also shown.
  • Fig. 9 shows a planet carrier, which has a tube with openings 3 for the planet, not shown, as a web 4, two cheeks 5, 8, a torsion disk as an outer cheek 2a, a hub 1, to which the torque is applied, reinforcing rings 18, 19 for receiving the Planetary axle bolt, an optional hub 7 for receiving a possible web bearing and an optional locking disc 16.
  • Fig. 9 also shows the arrangement of the weld seams 20 between the individual components. All welds 20 are welded through and closed.
  • Fig. 13 shows a planet carrier with a tube forming the webs 4, which projects on both ends of the planet carrier beyond the drive-side outer cheek 2a acting as a torsion disk and the driven-side cheek 5.
  • Fig. 14 shows a planet carrier with a tube forming the webs 4, which projects beyond the drive-side outer cheek 2a, which acts as a torsion disk.
  • the torsional stiffness of the planet carrier significantly influences the width-bearing behavior of the toothing. Because the drive-side inner cheek 8 having the drive-side axle seats 6a is separated from the torque-introducing hub 1, the shape of the drive-side inner cheek 8 can be varied such that the torsional deformation of the web 4, which leads to a rotational displacement of the driven-side cheek 5 and thus also of the output-side axle seat 6b, can be compensated.
  • Fig. 15 shows a side view of a planet carrier according to the invention with a drive-side hub 1, a driven-side hub 7 and a web 4 arranged therebetween Fig. 15 specified section XVI-XVI in Fig. 16 shown.
  • Fig. 16 shows a top view of the drive-side inner cheek 8 on the in Fig. 15 specified section XVI-XVI.
  • the cheek 8 has constrictions 22 between the axle seats 6a, it being possible for the depth of the constrictions 22 to vary the rigidity of the inner cheek 8 on the drive side.
  • Fig. 17 to 19 show possible designs of the cheeks 5, 8.
  • Fig. 17 shows a solid disc with a maximum stiffness, as it can preferably be used for the output side cheek 5.
  • Fig. 18 shows constrictions 22, 23 between the axle seats 6a, wherein the stiffness of the drive-side inner cheek 8 can be varied by a different depth of the constrictions 22, 23.
  • Fig. 19 shows a possible embodiment of how the stiffness variation of the drive-side inner cheek 8 can take place through cutouts 24 between the axle seats 6a.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)
  • Radio Relay Systems (AREA)
  • Soft Magnetic Materials (AREA)
  • Photovoltaic Devices (AREA)

Claims (10)

  1. Porte-satellite, comportant un moyeu (1) du côté menant, un flasque (2a) extérieur du côté menant, un flasque (5) du côté mené et au moins une entretoise (4) reliant les deux dits flasques (2a, 5), le flasque (5) du côté mené ayant au moins un siège (6b) d'axe du côté mené d'un axe (14) épicycloïdal, un flasque (8) intérieur du côté menant, qui est disposé parallèlement au flasque (2a) extérieur du côté menant et a au moins un siège (6a) d'axe du côté menant de l'axe (14) épicycloïdal, caractérisé en ce que le flasque (8) intérieur du côté menant est disposé entre le flasque (2a) extérieur du côté menant et le flasque (5) du côté mené.
  2. Porte-satellite suivant la revendication 1, dans lequel le flasque (8) intérieur du côté menant est fixé au moyeu (1) du côté menant et/ou au flasque (2a) extérieur du côté menant et/ou à la au moins une entretoise (4).
  3. Porte-satellite suivant l'une des revendications précédentes, dans lequel le porte-satellite est composé de plusieurs parties (1, 2a, 4, 5, 6a, 6b, 7, 8, 16) individuelles, notamment par des soudages ou des vissages.
  4. Porte-satellite suivant l'une des revendications précédentes, dans lequel le porte-satellite est composé de plusieurs partie (1, 2a, 4, 5, 6a, 6b, 7, 8, 16) individuelles par des soudages (20), dans lequel des encoches (21) de soulagement sont disposées le long d'au moins une partie de la longueur des soudages (20).
  5. Porte-satellite suivant l'une des revendications précédentes, dans lequel une pluralité d'entretoises (4) sont formées par un tuyau ayant des ouvertures (3).
  6. Porte-satellite suivant l'une des revendications précédentes, caractérisé en ce que le flasque (8) intérieur du côté menant a des resserrements (22, 23) et/ou des ouvertures entre les sièges (6a) d'axe du côté menant.
  7. Porte-satellite suivant l'une des revendications précédentes, caractérisé en ce que le flasque (5) du côté mené a des resserrements (22, 23) et/ou des ouvertures entre les sièges (6b) d'axe du côté mené.
  8. Porte-satellite suivant l'une des revendications précédentes, caractérisé en ce que le flaque (2a) extérieur du côté menant, le flasque (5) du côté mené et/ou le flasque (8) intérieur du côté menant sont constitués sous la forme de disques pleins, de roues à rayons ou de disques incurvés.
  9. Transmission d'éolienne, comprenant un porte-satellite, caractérisée en ce que le porte-satellite est constitué suivant l'une des revendications précédentes.
  10. Eolienne, comprenant une transmission d'éolienne, caractérisée en ce que la transmission d'éolienne est constituée suivant la revendication (7).
EP16184865.0A 2016-08-19 2016-08-19 Support epicycloïdal Active EP3284976B1 (fr)

Priority Applications (9)

Application Number Priority Date Filing Date Title
EP23166461.6A EP4219983A1 (fr) 2016-08-19 2016-08-19 Porte-satellites
ES20172987T ES2945582T3 (es) 2016-08-19 2016-08-19 Portasatélites
ES16184865T ES2806452T3 (es) 2016-08-19 2016-08-19 Soporte planetario
EP20172987.8A EP3708878B1 (fr) 2016-08-19 2016-08-19 Support epicycloïdal
DK16184865.0T DK3284976T3 (da) 2016-08-19 2016-08-19 Planetbærer
EP16184865.0A EP3284976B1 (fr) 2016-08-19 2016-08-19 Support epicycloïdal
DK20172987.8T DK3708878T3 (da) 2016-08-19 2016-08-19 Planetholder
CN201710707862.1A CN107763196B (zh) 2016-08-19 2017-08-17 行星架
US15/680,648 US10465791B2 (en) 2016-08-19 2017-08-18 Planetary carrier

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16184865.0A EP3284976B1 (fr) 2016-08-19 2016-08-19 Support epicycloïdal

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP23166461.6A Division EP4219983A1 (fr) 2016-08-19 2016-08-19 Porte-satellites
EP20172987.8A Division EP3708878B1 (fr) 2016-08-19 2016-08-19 Support epicycloïdal

Publications (2)

Publication Number Publication Date
EP3284976A1 EP3284976A1 (fr) 2018-02-21
EP3284976B1 true EP3284976B1 (fr) 2020-05-06

Family

ID=56740927

Family Applications (3)

Application Number Title Priority Date Filing Date
EP23166461.6A Pending EP4219983A1 (fr) 2016-08-19 2016-08-19 Porte-satellites
EP20172987.8A Active EP3708878B1 (fr) 2016-08-19 2016-08-19 Support epicycloïdal
EP16184865.0A Active EP3284976B1 (fr) 2016-08-19 2016-08-19 Support epicycloïdal

Family Applications Before (2)

Application Number Title Priority Date Filing Date
EP23166461.6A Pending EP4219983A1 (fr) 2016-08-19 2016-08-19 Porte-satellites
EP20172987.8A Active EP3708878B1 (fr) 2016-08-19 2016-08-19 Support epicycloïdal

Country Status (5)

Country Link
US (1) US10465791B2 (fr)
EP (3) EP4219983A1 (fr)
CN (1) CN107763196B (fr)
DK (2) DK3708878T3 (fr)
ES (2) ES2945582T3 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3502516A1 (fr) 2017-12-19 2019-06-26 Flender GmbH Engrenage planétaire, groupe motopropulseur et éolienne
DE102018109610A1 (de) * 2018-04-20 2019-10-24 Elringklinger Ag Planetenträger für ein Räderumlaufgetriebe wie einem Planetengetriebe und entsprechendes Stützverfahren
GB201917762D0 (en) 2019-12-05 2020-01-22 Rolls Royce Plc Reliable gearbox for gas turbine engine
GB201917760D0 (en) 2019-12-05 2020-01-22 Rolls Royce Plc Aircraft engine
CN215293537U (zh) 2021-04-21 2021-12-24 采埃孚(天津)风电有限公司 行星架及齿轮箱
FR3136533B1 (fr) 2022-06-10 2024-06-14 Safran Trans Systems Porte-satellites pour un reducteur mecanique de turbomachine d’aeronef

Citations (17)

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DE1198637B (de) 1961-12-23 1965-08-12 Demag Ag Umlaufraedergetriebe mit parallel angeordneten einfach schraegverzahnten Radsaetzen
JPS5813245A (ja) 1981-07-17 1983-01-25 Sumitomo Metal Ind Ltd 遊星歯車装置の荷重等配装置
EP1045140B1 (fr) 1999-04-12 2004-09-22 Winergy AG Boíte de vitesses pour éolienne
US20040259679A1 (en) 2003-04-04 2004-12-23 Hispano Suiza Flexible connection system between a planet carrier and the stationary support in a speed reduction gear train
DE10334824A1 (de) 2003-07-31 2005-05-19 Zf Friedrichshafen Ag Verbesserung der Lastverteilung in Planetengetrieben
WO2009083657A1 (fr) 2008-01-03 2009-07-09 Moventas Oy Agencement d'un mécanisme planétaire et d'un engrenage planétaire
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EP3708878B1 (fr) 2023-04-19
US20180051798A1 (en) 2018-02-22
DK3708878T3 (da) 2023-07-03
EP3284976A1 (fr) 2018-02-21
US10465791B2 (en) 2019-11-05
CN107763196B (zh) 2020-03-06
ES2806452T3 (es) 2021-02-17
DK3284976T3 (da) 2020-08-03
EP4219983A1 (fr) 2023-08-02
EP3708878A1 (fr) 2020-09-16
CN107763196A (zh) 2018-03-06
ES2945582T3 (es) 2023-07-04

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